Axially restraining torsional spring utilizing a tapered housing

ABSTRACT

A rotational and axial control spring includes a tubular casing, a shaft, and a plurality of elongated elastomeric members. The casing comprises a first end, a second end, and a plurality of interior surfaces extending therebetween defining a casing interior. The first end is smaller than the second end, forming a frustum shaped tubular casing. The cross sectional shape of the casing can include three (3) or more sides. The shaft is fabricated having a series of exterior surfaces, wherein a cross sectional shape of the shaft is similar to the cross sectional shape of the casing. The elastomeric members are formed as cylindrical frustums. The shaft is inserted within the casing interior. Each elastomeric member is positioned contacting a respective shaft exterior surface and a pair of adjacent casing interior surfaces. The elastomeric members each provide a rotational spring with adjustable resistant force and dampening functions. The tapered features provide an axial retention function.

FIELD OF THE INVENTION

The present invention relates to a device that manages torsional deflection and an axial force. More specifically, the device comprises a shaft retained within a casing by a series of conically shaped elastomeric elongated members, wherein the casing is formed having a trapezoid longitudinal cross sectional shaped interior surface contouring to surfaces of the series of conically shaped elastomeric elongated members.

BACKGROUND OF THE INVENTION Discussion of the Related Art

Rotational rubber springs or dampeners offer resistance in a torsional direction. Rotational rubber springs are commonly referred to as Neidhart springs. Neidhart springs are formed having a shaft retained within an interior of a tubular casing by a series of elastomeric elongated members. Each of the members is designed having a uniform cross sectional shape along their length. Each of the elastomeric elongated members is retained between and contacting a planar exterior surface of the shaft and each of two planar interior surfaces of the casing, wherein the two planar interior surfaces of the casing are joined by a common corner. In operation, as the assembly is subjected to a torsional force, the one of the shaft and casing is rotated respective to the other member. The rotational difference compresses each of the elastomeric elongated members. The compression generates a resistance to the applied torsional force. The resistance is provided in a form of a spring and a damper.

The currently known design has a significant limitation. The design has a uniform cross sectional shape extending along an entire length of the device. The elements are commonly fabricated using an extruding process, cut to length, then assembled by slideably inserting the shaft and elastomeric elongated members within the interior of the casing. Although the currently known design controls a torsional force by dampening rotational motion and returning the device to a neutral configuration, the uniform cross sectional shape fails to control any axial forces.

Thus, what is desired is a device that controls a torsional force by dampening rotational motion and returning the device to a neutral configuration, while additionally providing an axial constraint.

SUMMARY OF THE INVENTION

The present invention is directed to a device that controls a torsional force by dampening rotational motion and returning the device to a neutral configuration, while additionally providing an axial constraint.

In a first aspect of the present invention, a torsional spring and axial control device comprising:

a shaft having a plurality of planar exterior surfaces;

a series of elongated elastomeric members, each elongated elastomeric member having a first elastomeric member end and a second elastomeric member end, wherein a cross sectional area of the first elastomeric member end is smaller than a cross sectional area of the second elastomeric member end and a cross sectional shape of the body gradually transitions in size between the first elastomeric member end and the second elastomeric member end; and

a tubular casing comprising a plurality of planar interior surfaces defining a casing interior, wherein adjacent edges of adjacent pairs of planar interior surfaces are joined along an angular transition,

wherein said shaft is inserted within said casing interior and each of said series of elongated elastomeric members is positioned contacting one respective exterior planar shaft surface and a pair of adjacent interior planar casing surfaces, wherein said series of elongated elastomeric members provides a resistive rotational spring force between said shaft and said casing.

In a second aspect of the present invention, the gradual transition of the cross sectional shape of each of the elongated elastomeric members is linear along a length thereof.

In another aspect of the present invention, the gradual transition of the cross sectional shape of the tubular casing is linear along a length thereof.

In yet another aspect, the tubular casing is fabricated having a square frustum shape.

In yet another aspect, the shaft is fabricated having a uniform cross sectional shape.

In yet another aspect, the shaft is fabricated of a rigid material.

In yet another aspect, the shaft is fabricated of a pliant material.

In another aspect, the shaft is fabricated of a pliant material laminated upon an exterior surface of a rigid material.

In yet another aspect, the shaft is fabricated having a twisted configuration.

In yet another aspect, each of the external planar shaft surfaces has like transverse dimensions and each of the interior planar casing surfaces having like transverse dimensions.

In yet another aspect, the shaft comprises four external planar surfaces and the casing comprises four interior planar surfaces.

In yet another aspect, each of the four external planar shaft surfaces have like transverse dimensions and each of the four interior planar casing surfaces having like transverse dimensions.

In yet another aspect, the shaft comprises three external planar surfaces and the casing comprises three interior planar surfaces.

In yet another aspect, the shaft comprises five external planar surfaces and the casing comprises five interior planar surfaces.

In yet another aspect, the shaft comprises six external planar surfaces and the casing comprises six interior planar surfaces.

In yet another aspect, the shaft comprises n external planar surfaces and the casing comprises n interior planar surfaces, wherein n is selected from a number of surfaces group comprising three, four, five, six, and eight.

In another aspect, a first rotational and axial control spring is oriented proximate a second rotational and axial control spring, wherein like sized casing ends are positioned adjacent to one another.

In yet another aspect, the rotational and axial control spring further comprises an axial retention member. The axial retention member is preferably located proximate a smaller casing end.

In yet another aspect, tapered components of the rotational and axial control spring provides an axial control function limiting motion of a mating component to a single axial direction, wherein the single axial direction is from a larger casing cross sectional area towards a smaller casing cross sectional area.

In yet another aspect, tapered components of the rotational and axial control spring provides an axial control function limiting motion of the elongated elastomeric members to a single axial direction, wherein the single axial direction is from a smaller casing cross sectional area towards a larger casing cross sectional area.

In yet another aspect, tapered components of the rotational and axial control spring provides an axial control function limiting motion of a mating component to both axial directions.

In yet another aspect, tapered components of the rotational and axial control spring provides an axial control function limiting motion of the elongated elastomeric members to both axial directions.

The rotational and axial control spring provides several advantages over the currently available rotational rubber springs. Tapering the series of elongated elastomeric members and the respective shaft restricts axial motion of the shaft and elastomeric members in a first direction. By integrating a pair of oppositely oriented rotational and axial control springs into an assembly, the pair of rotational and axial control springs restricts axial motion of the shaft and elastomeric members in two directions. The elongated elastomeric members can be designed to optimize the dampening and spring rates by using the change in the cross sectional shape along the length thereof.

Another advantage over the currently available rotational rubber springs is that the tapered configuration reduces stress under torsional and axial loading.

These and other features, aspects, and advantages of the invention will be further understood and appreciated by those skilled in the art by reference to the following written specification, claims and appended drawings, which follow.

BRIEF DESCRIPTION OF THE DRAWINGS

For a fuller understanding of the nature of the present invention, reference should be made to the accompanying drawings in which:

FIG. 1 presents an isometric view of an exemplary rotational rubber spring in accordance with the known art;

FIG. 2 presents an end elevation view of the rotational rubber spring originally introduced in FIG. 1, the illustration presenting a shaft having a linear shape;

FIG. 3 presents an end elevation view of the rotational rubber spring originally introduced in FIG. 1, the illustration presenting a shaft having a twisted shape;

FIG. 4 presents an isometric view of an exemplary rotational and axial control spring;

FIG. 5 presents an end elevation view of the rotational and axial control spring originally introduced in FIG. 4, the illustration presenting a shaft having a linear shape;

FIG. 6 presents an end elevation view of the rotational and axial control spring originally introduced in FIG. 4, the illustration presenting a shaft having a twisted shape;

FIG. 7 presents an isometric exploded assembly view of the rotational and axial control spring introduced in FIG. 4;

FIG. 8 presents a side elevation view of a pair of rotational and axial control springs originally introduced in FIG. 4, the pair being oriented with like larger ends positioned adjacent to one another;

FIG. 9 presents a side elevation view of a pair of rotational and axial control springs originally introduced in FIG. 4, the pair being oriented with like smaller ends positioned adjacent to one another;

FIG. 10 presents a sectioned side elevation view of the rotational and axial control spring originally introduced in FIG. 4, the section being taken along a vertical wall of the tubular casing;

FIG. 11 presents an end elevation view of another exemplary rotational rubber spring wherein the shaft comprises three external planar surfaces and the casing comprises three interior planar surfaces;

FIG. 12 presents an end elevation view of another exemplary rotational rubber spring wherein the shaft comprises five external planar surfaces and the casing comprises five interior planar surfaces; and

FIG. 13 presents an end elevation view of another exemplary rotational rubber spring wherein the shaft comprises six external planar surfaces and the casing comprises six interior planar surfaces.

Like reference numerals refer to like parts throughout the several views of the drawings.

DETAILED DESCRIPTION OF THE INVENTION

The following detailed description is merely exemplary in nature and is not intended to limit the described embodiments or the application and uses of the described embodiments. As used herein, the word “exemplary” or “illustrative” means “serving as an example, instance, or illustration.” Any implementation described herein as “exemplary” or “illustrative” is not necessarily to be construed as preferred or advantageous over other implementations. All of the implementations described below are exemplary implementations provided to enable persons skilled in the art to make or use the embodiments of the disclosure and are not intended to limit the scope of the disclosure, which is defined by the claims. For purposes of description herein, the terms “upper”, “lower”, “left”, “rear”, “right”, “front”, “vertical”, “horizontal”, and derivatives thereof shall relate to the invention as oriented in FIG. 1. Furthermore, there is no intention to be bound by any expressed or implied theory presented in the preceding technical field, background, brief summary or the following detailed description. It is also to be understood that the specific devices and processes illustrated in the attached drawings, and described in the following specification, are simply exemplary embodiments of the inventive concepts defined in the appended claims. Hence, specific dimensions and other physical characteristics relating to the embodiments disclosed herein are not to be considered as limiting, unless the claims expressly state otherwise.

An exemplary rotational rubber spring 100, in accordance with known prior art is illustrated in FIGS. 1 through 3. The rotational rubber spring 100 integrates a tubular casing 110, a shaft 120, and a series of elongated elastomeric members 130 into a single assembly. The tubular casing 110 has a tubular cross section forming an equilateral convex polygon shape spanning between a first casing end 112 and a second casing end 114. The tubular casing 110 is designed having a uniform cross sectional shape extending a length thereof. Due to the uniform cross sectional area and low manufacturing cost, the tubular casing 110 is commonly manufactured using an extrusion process. The tubular casing 110 is preferably fabricated of a rigid material, such as plastic, metal, a composite, and the like. The interior of the tubular casing 110 defines a plurality of casing interior planar surfaces 116, wherein mating edges of each pair of adjacently located casing interior planar surfaces 116 forms a casing interior angular transition 118. The plurality of casing interior planar surfaces 116 defines a periphery of a casing interior volume. The exemplary embodiment includes four (4) equally dimensioned casing interior planar surfaces 116.

The shaft 120 has a cross section forming an equilateral convex polygon shape spanning between a shaft first end surface 122 and a shaft second end surface 124. The shape of the shaft cross section is similar to the cross sectioned shape of the casing cross section. An exterior of the shaft 120 is defined by a shaft first end surface 122 located at a first longitudinal end, a shaft second end surface 124 located as a second, opposite longitudinal end, and a plurality of shaft external longitudinal surfaces 126 spanning therebetween. The number of shaft external longitudinal surfaces 126 equals the number of casing interior planar surfaces 116. The shaft 120 is designed having a uniform cross sectional shape extending a length thereof. Like the tubular casing 110, due to the uniform cross sectional area and low manufacturing cost, the shaft 120 is commonly manufactured using an extrusion process. The shaft 120 is commonly fabricated of a pliant material. The shaft 120 is inserted into an interior of the tubular casing 110. The shaft 120 is rotated aligning each shaft external longitudinal surface 126 with a respective casing interior angular transition 118.

Each of the elongated elastomeric member 130 is designed having a uniform cross sectional shape extending along a length defined between an elongated elastomeric member first end surface 132 and an elongated elastomeric member second end surface 134. The exposed surface spanning between the elongated elastomeric member first end surface 132 and the elongated elastomeric member second end surface 134 is referred to as an elongated member exterior surface 136. The elongated elastomeric member 130 is fabricated of a rubber or other resilient material. Like the tubular casing 110 and shaft 120, due to the uniform cross sectional area and low manufacturing cost, the elongated elastomeric member 130 is commonly manufactured using an extrusion process. The elongated elastomeric member 130 can be fabricated having a circular or elliptical cross sectional shape.

In use, the elongated member exterior surface 136 of each elongated elastomeric member 130 engages with the respective shaft external longitudinal surface 126 and a pair of respective casing interior planar surfaces 116. The three contact points refrain rotation of the shaft 120 respective to the tubular casing 110 when subjected to a torsional force in a direction of a rotational motion 150. The shaft 120 deforms forming a shaft second end surface 124 in the area engaging with the respective elongated elastomeric member 130. When undergoing the rotational motion 150, the pliancy of the elongated elastomeric member 130 enables incremental rotation of the shaft 120 respective to the tubular casing 110. As the motion continues, the elongated elastomeric member 130 is compressed, wherein the compression of the elongated elastomeric member 130 increases the resistance of the rotational motion 150. In addition, the rotational motion 150 utilizes each elongated elastomeric member 130 as a wedge, thus further increasing the resistance to the rotational motion 150. When the torsional force is removed, the pliancy of each the series of elongated elastomeric members 130 returns the shaft 120 to a natural, relaxed position.

In an alternative embodiment, the rotational rubber spring 100 can include a twisted shaft 121, which includes a shaft elastomeric engaging deformation 129 for engaging with each elongated elastomeric member 130. The twisted section of the twisted shaft 121 increase the interaction between the twisted shaft 121 and the elongated elastomeric member 130. Additionally, the shape of the twisted shaft 121 increases the rotational distance of the twisted shaft 121 within the rotational rubber spring 100.

One limitation of the rotational rubber spring 100 is the freedom of motion in an axial direction, identified as axial motion 140. The uniform cross sectional shape enables axial motion of the various components and/or other mating equipment.

An exemplary rotational and axial control spring, identified by reference number 200, is presented in FIGS. 4 through 7. The rotational and axial control spring 200 includes elements having a tapered shape introducing an axial control feature.

The rotational and axial control spring 200 integrates a tubular casing 210, a shaft 220, and a series of elongated elastomeric members 230 into a single assembly. The tubular casing 210 is formed into a square frustum tubular shape. A first casing end 212 defines a first end of the tubular casing 210 and a second casing end 214 defines a second end of the tubular casing 210. The first casing end 212 has a smaller cross sectional area compared to a cross sectional area of the second casing end 214 and the cross sectional shape gradually transitions in size between the first casing end 212 and the second casing end 214. In one embodiment, the tubular casing 210 is cross sectional shape has a linear transition between the first casing end 212 and the second casing end 214. The square frustum tubular shape can be formed using any manufacturing processes known by those skilled in the art, including molding, punching, bending, and the like. The tubular casing 210 is preferably fabricated of a rigid material, such as plastic, metal, a composite, and the like. The interior of the tubular casing 210 defines a plurality of casing interior planar surfaces 216, wherein mating edges of each pair of adjacently located casing interior planar surfaces 216 forms a casing interior angular transition 218. The plurality of casing interior planar surfaces 216 defines a periphery of a casing interior volume. The exemplary embodiment includes four (4) equally dimensioned casing interior planar surfaces 216.

The shaft 220 has a cross section forming an equilateral convex polygon shape spanning between a shaft first end surface 222 and a shaft second end surface 224. The cross section shape of the shaft is similar to the cross sectioned shape of the casing. A series of shaft external longitudinal surfaces 226 spans between the shaft first end surface 222 and shaft second end surface 224 of the shaft 220. The number of shaft external longitudinal surfaces 226 equals the number of casing interior planar surfaces 216. The shaft 220 is designed having a uniform cross sectional shape extending a length thereof. Due to the uniform cross sectional area and low manufacturing cost, the shaft 220 is commonly manufactured using an extrusion process. The shaft 220 can be fabricated of a pliant material, a rigid material, or a pliant covered rigid material, such as a laminated elastomeric coating 228 applied over a rigid core.

Each elongated elastomeric member 230 is formed into a conical frustum shape. An elongated elastomeric member first end surface 232 defines a first end of the elongated elastomeric member 230 and an elongated elastomeric member second end surface 234 defines a second end of the elongated elastomeric member 230, wherein the elongated elastomeric member first end surface 232 is smaller than the elongated elastomeric member second end surface 234. An elongated member exterior surface 236 spans between a circumferential edge of the elongated elastomeric member first end surface 232 and a circumferential edge of the elongated elastomeric member second end surface 234. The exemplary elongated elastomeric member 230 is shaped having a rounded cross sectional shape, wherein the cross sectional shape can be elliptical, circular, and the like. It is understood that the cross sectional shape can also be formed having a triangular cross sectional shape, or a combination of a cornered segment and a rounded segment. The elongated elastomeric member 230 is preferably designed having a circular or elliptical cross sectional shape. The sidewall of the elongated elastomeric member 230 is formed having a gradually transition in the cross sectional shape extending between a peripheral edge of the elongated elastomeric member first end surface 232 and a peripheral edge of the elongated elastomeric member second end surface 234. The preferred transition between the elongated elastomeric member first end surface 232 and the elongated elastomeric member second end surface 234 is linear. It is also understood that the transition between the elongated elastomeric member first end surface 232 and the elongated elastomeric member second end surface 234 can be of any suitable shape, including an arched section, a series of rings, fingers, and the like. When the elongated elastomeric member 230 is positioned contacting the shaft external longitudinal surface 226, the angle formed by a distal surface of the conical frustum shape of the elongated elastomeric member 230 coincides with the angle defined by the casing interior planar surface 216 of the tubular casing 210.

Each elongated elastomeric member 230 can be optimized to suit the target application. The elastomer hardness or modulus can be varied to obtain different torsional and axial resistance or spring rate in the same design envelope. Low modulus rubber would provide a soft spring, where as high modulus rubber would provide a very stiff spring. Typical hardness could include, but are not limited to, 20 Shore A durometer up to 60 Shore D durometer. A corresponding compressive or shear modulus range could be 20 psi to 1000 psi. The material for the elongated elastomeric members 230 can be selected from any of a variety of rubber, plastic, or other polymeric materials to obtain optimal properties of spring rate, fluid, environmental resistance, and the like. The elongated elastomeric member 230 is fabricated of any elastomeric or resilient material, including natural rubber, synthetic rubber, Nitrile, polyurethane, EPDM, silicone, fluoroelastomer, Epichlorohydrin, SBR, Polybutadiene, neoprene, thermoplastic elastomers, elastin, and the like.

The assembly of the rotational and axial control spring 200 is best represented in the exploded assembly view illustrated in FIG. 7. The rotational and axial control spring 200 is assembled by inserting the shaft 220 into an interior section of the tubular casing 210. The shaft 220 is rotated aligning each shaft external longitudinal surface 226 with a respective casing interior angular transition 218. The rotational and axial control spring 200 includes one elongated elastomeric member 230 for each shaft external longitudinal surface 226 of the shaft 220. One elongated elastomeric member 230 is installed contacting a respective shaft external longitudinal surface 226 and a pair of adjacently located casing interior planar surfaces 216 for each of the shaft external longitudinal surfaces 226.

In use, each elongated member exterior surface 236 of the respective elongated elastomeric member 230 engages with the respective shaft external longitudinal surface 226 and a pair of respective casing interior planar surfaces 116. The three contact points refrain rotation of the shaft 220 respective to the tubular casing 210 when subjected to a torsional force in a direction of a rotational motion 250. When undergoing the rotational motion 250, the pliancy of the elongated elastomeric member 230 enables incremental rotation of the shaft 220 respective to the tubular casing 210. As the motion continues, the elongated elastomeric member 230 is compressed, wherein the compression of the elongated elastomeric member 230 increases the resistance of the rotational motion 250. In addition, the rotational motion 250 utilizes each elongated elastomeric member 230 as a wedge, thus further increasing the resistance to the rotational motion 250. When the torsional force is removed, the pliancy of each the series of elongated elastomeric members 230 returns the shaft 220 to a natural, relaxed position.

In an alternative embodiment, the rotational and axial control spring 200 can include a twisted shaft 221, which includes a shaft elastomeric engaging deformation 229 for engaging with each elongated elastomeric member 230. The twisted section of the twisted shaft 221 increase the interaction between the twisted shaft 221 and the elongated elastomeric member 230. Additionally, the shape of the twisted shaft 221 increases the rotational distance of the twisted shaft 221 within the rotational and axial control spring 200. It is noted, twisted cams are limited, wherein the torsion resistance differs respective to the rotational direction, more specifically the torsional resistance differs between a clockwise or counterclockwise rotation. Additionally, the maximum rotation is also limited differently in clockwise or counterclockwise rotation.

One unique advantage of the rotational and axial control spring 200 over the rotational rubber spring 100 is the inclusion of the tapered shape. The square frustum shape of the tubular casing 210 restricts axial motion 240 to a direction from the second casing end 214 towards the first casing end 212. The restriction prevents the shaft 220 and/or any of the elongated elastomeric members 230 from moving axially or “walking out” of the interior chamber of the tubular casing 210 while in an application that is subjected to a combination of a torsional load and an axial load. Another advantage is the ability to shape each of the elongated elastomeric members 230 to fine-tune the dampening coefficient and the spring rate. The thickness, the density of the material, the shape of the sidewall 236, and the like can refine the characteristics of the elongated elastomeric member 230.

By arranging each of a pair of rotational and axial control springs 200 abutting like ends of one another along the longitudinal axis, as illustrated in FIGS. 8 and 9, the pair restrains motion along the axial motion 240 in both directions. Each of the pair of rotational and axial control springs 200 can be arranged orienting the second casing ends 214 abutting one another as illustrated in FIG. 8 or having each of the pair of rotational and axial control springs 200 arranged orienting the first casing ends 212 abutting one another as illustrated in FIG. 9. It is understood that the pair of rotational and axial control springs 200 can be joined together or integrated into a single unit. An integrated unit would join the pair of tubular casings 210 together and the pair of shafts 220 together.

An optional axial retention member 242 can be integrated into the rotational and axial control spring 200 as illustrated in FIG. 10 to enhance axial control of the shaft 220. The axial retention member 242 is included to provide additional axial restraint to the shaft 220 within the tubular casing 210.

Although the exemplary rotational and axial control spring 200 is configured having four (4) equally sized casing interior planar surfaces 216, it is understood that the rotational and axial control spring can be configured having three (3) or more equally sized casing interior planar surfaces 116, wherein one skilled in the art would recognize that the greater the number of sides, the lower the allowable rotational angle. Several examples are presented in FIGS. 11 through 13.

A triangular shaped rotational and axial control spring 300 is presented in FIG. 11. The triangular shaped rotational and axial control spring 300 is similar to the rotational and axial control spring 200, wherein the distinction is the number of sides. The triangular shaped rotational and axial control spring 300 is designed having three (3) equally dimensioned sides and the rotational and axial control spring 200 has four (4) equally dimensioned sides. Like features of the triangular shaped rotational and axial control spring 300 and the rotational and axial control spring 200 are numbered the same except preceded by the numeral ‘3’. The triangular shaped rotational and axial control spring 300 would be configured incorporating like tapered features of the rotational and axial control spring 200 as previously described.

A pentagonal shaped rotational and axial control spring 400 is presented in FIG. 12. The pentagonal shaped rotational and axial control spring 400 is similar to the rotational and axial control spring 200, wherein the distinction is the number of sides. The pentagonal shaped rotational and axial control spring 400 is designed having five (5) equally dimensioned sides and the rotational and axial control spring 200 has four (4) equally dimensioned sides Like features of the hexagonal shaped rotational and axial control spring 500 and the rotational and axial control spring 200 are numbered the same except preceded by the numeral ‘5’. The pentagonal shaped rotational and axial control spring 400 would be configured incorporating like tapered features of the rotational and axial control spring 200 as previously described.

A hexagonal shaped rotational and axial control spring 500 is presented in FIG. 13. The hexagonal shaped rotational and axial control spring 500 is similar to the rotational and axial control spring 200, wherein the distinction is the number of sides. The hexagonal shaped rotational and axial control spring 500 is designed having six (6) equally dimensioned sides and the rotational and axial control spring 200 has four (4) equally dimensioned sides. Like features of the hexagonal shaped rotational and axial control spring 500 and the rotational and axial control spring 200 are numbered the same except preceded by the numeral ‘5’. The hexagonal shaped rotational and axial control spring 500 would be configured incorporating like tapered features of the rotational and axial control spring 200 as previously described.

Although the exemplary embodiments present rotational and axial control springs having three (3), four (4), five (5), and six (6) sides, it is understood that the rotational and axial control spring can be designed to have seven (7), eight (8), nine (9), ten (10) or more sides. The greater the number of sides, the lower the maximum torsional rotation. The rotation is limited to a maximum deflection of one-half of a rotation from the original position (wherein the shaft external longitudinal surface 226 is aligned with the casing interior angular transition 218) towards a second indexed original position (wherein the shaft external longitudinal surface 226 is aligned with an adjacent casing interior angular transition 218). In other words, wherein the rotation of the shaft 220 is from an original position where the shaft external longitudinal surface 226 is aligned with the casing interior angular transition 218 to a position where the shaft external longitudinal surface 226 is in registration with a facing casing interior planar surface 216. The following table presents a maximum torsional rotation respective to the number of shaft external longitudinal surfaces 226.

TABLE ROTATION BASED UPON NUMBER OF SIDES OF SPRING Cross Sectional Number of Maximum Shape Sides Degree of Rotation Triangular 3 60 Degrees Square 4 45 Degrees Pentagon 5 36 Degrees Hextagon 6 30 Degrees

The exemplary embodiment presents a rotational and axial control spring 200 including an elongated elastomeric member 230 fabricated of an elastomeric material. It is understood that the elongated elastomeric member 230 can actually be fabricated of a rigid material or having the elastomeric material laminated upon a rigid material. The spring and dampening functions would be provided by a shaft 210 fabricated of an elastomeric material.

Since many modifications, variations, and changes in detail can be made to the described preferred embodiments of the invention, it is intended that all matters in the foregoing description and shown in the accompanying drawings be interpreted as illustrative and not in a limiting sense. Thus, the scope of the invention should be determined by the appended claims and their legal equivalence.

LISTING OF REFERENCE NUMBERS Ref. No. Description 100 rotational rubber spring 110 tubular casing 112 first casing end 114 second casing end 116 casing interior planar surface 118 casing interior angular transition 120 shaft 121 twisted shaft 122 shaft first end surface 124 shaft second end surface 126 shaft external longitudinal surface 127 twisted shaft external longitudinal surface 129 shaft twisted feature 130 elongated elastomeric member 132 elongated elastomeric member first end surface 134 elongated elastomeric member second end surface 136 elongated member exterior surface 140 axial motion 150 rotational motion 200 rotational and axial control spring 210 tubular casing 212 first casing end 214 second casing end 216 casing interior planar surface 218 casing interior angular transition 220 shaft 221 twisted shaft 222 shaft first end surface 224 shaft second end surface 226 shaft external longitudinal surface 227 twisted shaft external longitudinal surface 228 laminated elastomeric coating 229 shaft twisted feature 230 elongated elastomeric member 232 elongated elastomeric member first end surface 234 elongated elastomeric member second end surface 236 elongated member exterior surface 240 axial motion 242 axial retention member 250 rotational motion 300 triangular shaped rotational and axial control spring 310 tubular triangular shaped casing 312 casing end 316 casing interior planar surface 318 casing interior angular transition 320 shaft 330 elongated elastomeric member 400 pentagonal shaped rotational and axial control spring 410 tubular pentagonally shaped casing 412 casing end 416 casing interior planar surface 418 casing interior angular transition 420 shaft 430 elongated elastomeric member 500 hexagonal shaped rotational and axial control spring 510 tubular hexagonally shaped casing 512 casing end 516 casing interior planar surface 518 casing interior angular transition 520 shaft 530 elongated elastomeric member 

What is claimed is:
 1. A torsional spring and axial control device, comprising: a shaft having a plurality of planar exterior surfaces; a series of elongated elastomeric members, each elongated elastomeric member having a first elastomeric member end and a second elastomeric member end, wherein a cross sectional area of said first elastomeric member end is smaller than a cross sectional area of said second elastomeric member end and a cross sectional shape of said body gradually transitions in size between said first elastomeric member end and said second elastomeric member end; and a tubular casing comprising a plurality of planar interior surfaces, wherein adjacent edges of adjacent pairs of planar interior surfaces are joined along an angular transition, said plurality of planar interior surfaces collectively defining a tapered casing interior, said tubular casing having a cross sectional geometry of a first size at a first end and a same cross sectional geometry of a second size at a second, opposite end, wherein said first cross sectional geometry size is smaller than said second cross sectional geometry size, wherein each of said plurality of planar interior surfaces are trapezoidal and equal in size and shape, wherein said shaft is inserted within said tapered casing interior and each of said series of elongated elastomeric members is positioned contacting one respective exterior planar shaft surface and a pair of adjacent interior planar casing surfaces, wherein a resulting central axis of each of said tapered elongated elastomeric members are arranged to converge upon a central axis of said shaft, and wherein said series of elongated elastomeric members provides a resistive rotational spring force between said shaft and said casing.
 2. A torsional spring and axial control device as recited in claim 1, wherein said shaft has a uniform cross sectional shape along a length thereof.
 3. A torsional spring and axial control device as recited in claim 1, wherein said gradual transition in size between said first elastomeric member end and said second elastomeric member end is linear along a length thereof.
 4. A torsional spring and axial control device as recited in claim 1, wherein said gradual transition in size between said first tubular casing end and said second tubular casing end is linear along a length thereof.
 5. A torsional spring and axial control device as recited in claim 4, wherein said gradual transition in size between said first elastomeric member end and said second elastomeric member end is linear along a length thereof.
 6. A torsional spring and axial control device as recited in claim 1, wherein said tubular casing is formed having a square frustum shape.
 7. A torsional spring and axial control device as recited in claim 1, wherein said tubular casing is formed n number of sides and said shaft is formed having n number of shaft exterior surfaces, wherein n is selected from a group consisting of: a) three (3) sides, b) four (4) sides, c) five (5) sides, and d) six (6) sides.
 8. A torsional spring and axial control device, comprising: a shaft having a plurality of planar exterior surfaces, wherein said shaft has a uniform cross sectional shape along a length thereof; a series of elongated elastomeric members, each elongated elastomeric member having a first elastomeric member end and a second elastomeric member end, wherein a cross sectional area of said first elastomeric member end is smaller than a cross sectional area of said second elastomeric member end and a cross sectional shape of said body which gradually transitions in size between said first elastomeric member end and said second elastomeric member end; and a tubular casing comprising a first tubular shaped casing end, a second tubular shaped casing end, and a plurality of planar interior surfaces extending between an interior edge of said first tubular shaped casing end and said second tubular shaped casing end, wherein adjacent edges of adjacent pairs of planar interior surfaces are joined along an angular transition, said plurality of planar interior surfaces collectively defining a tapered casing interior, said tubular casing having a cross sectional geometry of a first size at a first end and a same cross sectional geometry of a second size at a second, opposite end, wherein said first cross sectional geometry size is smaller than said second cross sectional geometry size, wherein each of said plurality of planar interior surfaces are trapezoidal and equal in size and shape, wherein said shaft is inserted within said casing interior and each of said series of elongated elastomeric members is positioned contacting one respective exterior planar shaft surface and a pair of adjacent interior planar casing surfaces, wherein a resulting central axis of each of said tapered elongated elastomeric members are arranged to converge upon a central axis of said shaft, and wherein said series of elongated elastomeric members provides a resistive rotational spring force between said shaft and said casing.
 9. A torsional spring and axial control device as recited in claim 8, wherein said shaft is configured as a twisted shaft.
 10. A torsional spring and axial control device as recited in claim 8, wherein said gradual transition in size between said first elastomeric member end and said second elastomeric member end is linear along a length thereof.
 11. A torsional spring and axial control device as recited in claim 8, wherein said gradual transition in size between said first tubular casing end and said second tubular casing end is linear along a length thereof.
 12. A torsional spring and axial control device as recited in claim 11, wherein said gradual transition in size between said first elastomeric member end and said second elastomeric member end is linear along a length thereof.
 13. A torsional spring and axial control device as recited in claim 8, wherein said tubular casing is formed having a square frustum shape.
 14. A torsional spring and axial control device as recited in claim 8, wherein said tubular casing is formed n number of sides and said shaft is formed having n number of shaft exterior surfaces, wherein n is selected from a group consisting of: a) three (3) sides, b) four (4) sides, c) five (5) sides, and d) six (6) sides.
 15. A torsional spring and axial control device, comprising: a pair of torsional spring and axial control subassemblies, each torsional spring and axial control subassembly comprising: a shaft having a plurality of planar exterior surfaces; a series of elongated elastomeric members, each elongated elastomeric member having a first elastomeric member end and a second elastomeric member end, wherein a cross sectional area of said first elastomeric member end is smaller than a cross sectional area of said second elastomeric member end and a cross sectional shape of said body which gradually transitions in size between said first elastomeric member end and said second elastomeric member end; and a tubular casing comprising a plurality of planar interior surfaces, wherein adjacent pairs of planar interior surfaces are joined at an angular transition, said plurality of planar interior surfaces collectively defining a tapered casing interior, said tubular casing having a cross sectional geometry of a first size at a first end and a same cross sectional geometry of a second size at a second, opposite end, wherein said first cross sectional geometry size is smaller than said second cross sectional geometry size, wherein each of said plurality of planar interior surfaces are trapezoidal and equal in size and shape, wherein said shaft is inserted within said tapered casing interior and each of said series of elongated elastomeric members is positioned contacting one respective exterior planar shaft surface and a pair of adjacent interior planar casing surfaces, wherein a resulting central axis of each of said tapered elongated elastomeric members are arranged to converge upon a central axis of said shaft, and wherein said series of elongated elastomeric members provides a resistive rotational spring force between said shaft and said casing, wherein said pair of rotational and axial control springs are arranged having said rotational and axial control springs oriented abutting like ends with one another, said pair of rotational and axial control springs being oriented forming a continuous and linear longitudinal axis.
 16. A torsional spring and axial control device as recited in claim 15, wherein said shaft has a uniform cross sectional shape along a length thereof.
 17. A torsional spring and axial control device as recited in claim 15, wherein said gradual transition in size between said first elastomeric member end and said second elastomeric member end is linear along a length thereof.
 18. A torsional spring and axial control device as recited in claim 15, wherein said gradual transition in size between said first tubular casing end and said second tubular casing end is linear along a length thereof.
 19. A torsional spring and axial control device as recited in claim 15, wherein said shaft is configured as a twisted shaft.
 20. A torsional spring and axial control device as recited in claim 15, wherein said tubular casing is formed n number of sides and said shaft is formed having n number of shaft exterior surfaces, wherein n is selected from a group consisting of: a) three (3) sides, b) four (4) sides, c) five (5) sides, and d) six (6) sides. 